EP2373908B1 - Arbre d'equilibrage - Google Patents

Arbre d'equilibrage Download PDF

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Publication number
EP2373908B1
EP2373908B1 EP09764783.8A EP09764783A EP2373908B1 EP 2373908 B1 EP2373908 B1 EP 2373908B1 EP 09764783 A EP09764783 A EP 09764783A EP 2373908 B1 EP2373908 B1 EP 2373908B1
Authority
EP
European Patent Office
Prior art keywords
shaft
balancing shaft
pins
bearing journal
balancing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP09764783.8A
Other languages
German (de)
English (en)
Other versions
EP2373908A1 (fr
Inventor
Peter Solfrank
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2373908A1 publication Critical patent/EP2373908A1/fr
Application granted granted Critical
Publication of EP2373908B1 publication Critical patent/EP2373908B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
    • F16F15/264—Rotating balancer shafts

Definitions

  • the invention relates to a balance shaft for balancing mass forces and / or moments of inertia of an internal combustion engine.
  • the balance shaft comprises at least one imbalance section with center of gravity extending eccentrically to the shaft axis and at least one bearing pin for the radial mounting of the balance shaft in the internal combustion engine.
  • the unbalance portion and the bearing pin made of different materials are made separately from each other and then axially joined together by means of a torsionally rigid pin / hole connection.
  • Such a balance shaft in which the unbalance portion and the one or more journals are made of appropriate underschtedlichen materials, goes out of the DE 44 12 476 A1 .
  • the journals aligned in a shaft axis Insert holes at the longitudinal ends of the imbalance section firmly and accordingly produce a positive connection between these components.
  • the required fatigue strength of this pin / hole connection requires, in particular with regard to the sometimes not insignificant torsional vibrations in the balance shaft drive and the rotational inertia of the balance shaft a particularly high and therefore costly surface and dimensional accuracy of the components to permanently rule out their relative rotations can.
  • the present invention is therefore the object of a joined balancing shaft of the type mentioned in such a way that their components by means of an improved pin / hole connection are permanently secured against rotation against each other.
  • the pin / bore connection should be formed positively acting in the direction of rotation of the balance shaft and having at least two pins and associated holes which extend eccentrically to the shaft axis.
  • the rotational connection between the unbalance portions and the one or more bearing journals not - as provided in the prior art - non-positively, but by means of eccentric to the shaft axis arranged pins and associated holes form-fitting acting.
  • the material of the journal should be a roller bearing steel, wherein the journal serves as an inner race for the rolling elements of a rolling bearing.
  • rolling bearing steel the grades C16, 16MnCr5, C45, Cf53, C80 and 100Cr6 in particular come into consideration.
  • roller bearings with balancing shafts offer the potential of significantly reduced bearing friction compared to conventional plain bearings.
  • this potential can be exploited in a particularly cost-effective manner, in that only the one or more bearing journals consist of the roller bearing steel, while the one or more imbalance sections are made of significantly less expensive casting material.
  • the bearing pin has a variable width over its circumference in the direction of the shaft axis.
  • the journal is in a load zone in which the bearing pin is acted upon by the circumferential axis of the balancing radial load of the imbalance section, have a first width and outside the load zone either a second width having significantly tapers or interrupted on the circumference, the pins and the associated holes are eccentric towards the load zone.
  • FIGS EP 1 775 484 A2 with tapered journals or on the WO 2007/121861 A1 referenced with interrupted trunnions - can be added according to the invention, however, particularly advantageous with the or unbalanced sections, since the load zone, ie the larger width of the journal out eccentric pins and associated holes despite decreasing width of the journal with a correspondingly large length of support are executable. The largest possible support length results in the case when the pins and the associated holes extend completely within the first width of the journal.
  • two identically shaped bearing journals can be provided, which are joined with both longitudinal ends of the unbalanced portion, wherein the bearing pin joined to a drive side longitudinal end of the unbalanced portion and a separately manufactured drive element of the balance shaft are axially joined together by means of another torsionally rigid pin / hole connection and wherein the further pin / hole connection is also formed positively acting in the direction of rotation of the balance shaft and has at least two pins and associated bores, which extend eccentrically to the shaft axis.
  • pin / bore connections each have exactly two identically designed pins and associated holes which extend to a plane defined by the shaft axis and the center of gravity of the imbalance section longitudinal symmetry plane of the balance shaft substantially mirror-symmetrical.
  • a balance shaft 1 to compensate for inertial forces and or inertia of an internal combustion engine in the assembly or exploded view disclosed.
  • the balancing shaft 1 is joined from separately produced components and consists of an unbalanced section 2 with eccentric to the shaft axis 3 extending center of gravity 4 and two journals 5 and 6, which are connected to both longitudinal ends of the unbalanced section 2, and from a drive element 7, with the bearing pin 5 is connected to the drive-side longitudinal end of the imbalance section 2, together.
  • the drive element 7 serves to receive a chain or gear, not shown, for rotational coupling of the balance shaft 1 with the crankshaft of the internal combustion engine.
  • the two identically designed bearing journals 5, 6 and the unbalanced section 2 are joined by means of torsionally rigid pin / bore connections on the end side axially adjacent to each other, wherein the pin / hole connections are formed positively acting in the direction of rotation of the balancer shaft 1. They have for this purpose in each case two cylindrical pins 8, 9 and 10, 11 and associated bores 12, 13, 14, 15 and 16, 17, 18, 19, which extend eccentrically to the shaft axis 3. Each of the pins 8 to 11 is press-fitted in the associated bores 12 to 19 in the bearing journals 5, 6 and in the imbalance section 2 in order to fix the said components axially together.
  • pins 20, 21 and the associated bores 12, 14, 22 and 23 are provided for this purpose.
  • the pins 8, 10, 20 with the associated bores 12, 13, 16, 17, 22 and the pins 9, 11, 21 with the associated bores 14, 15, 18, 19, 23 extend on common axes 24 and 25, respectively which extend mirror-symmetrically to a longitudinal symmetry plane 26 of the balancing shaft 1 spanned by the shaft axis 3 and the center of mass 4 of the imbalance section 2 (see FIG FIG. 1 ).
  • the pins 8, 9 and 10, 11 and 20, 21 are each identical to each other, as an alternative embodiment, the possibility exists, the successive Replace pins 8 and 20 as well as 9 and 21 with two appropriately extended pins.
  • the bearing pins 5, 6 are produced as forgings from a bearing steel of the aforementioned varieties and each form a wear-resistant inner race for the rolling elements of a rolling bearing, not shown, by means of which the balance shaft 1 radially is stored in the internal combustion engine.
  • the bearing journals 5, 6 Because of the radial load of the imbalance section 2 revolving with the balancing shaft 1, a load zone resting thereon is formed on the bearing journals 5, 6, the loading of which is determined by a circumferential section of the bearing journals 5, 6 (in the present illustration: their underside) decreases. In conjunction with said roller bearing of the balance shaft 1, this provides the possibility of providing the bearing journals 5, 6 with a width which varies over the circumference thereof in the direction of the shaft axis 3. In the illustrated embodiment, the bearing journals 5, 6 have a first width 28 which extends symmetrically to the load zone over a circumference of about 200 ° and outside of this area merges under distinct tapering into a second width 29.
  • the bearing pins 5, 6 respectively at that of the load zone, i. the peripheral portion 27 opposite and not or at most only slightly loaded peripheral area to interrupt, so that then the inner race for the rolling elements would not extend over a full angle of 360 °.
  • the axes 24, 25 are eccentric to the center of gravity 4, ie the load zone, the pins 8 to 11 and 20, 21 and the associated holes 12 to 19 completely within the first Width 28 of the bearing pin 5, 6 run.
  • the diameter of the bearing journals 5, 6 and the enveloping circle of the imbalance section 2 are dimensioned such that the outer enveloping circle of the rolling elements is smaller than the enveloping circle of the imbalance section 2.
  • the balancer shaft 1 with WälzSystem principles mounted on the bearing pin 5, 6 (eg needles and needle cage) and outer rings whose diameter is greater than the outer circle of the imbalance section 2, to equip.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Claims (6)

  1. Arbre d'équilibrage (1) pour équilibrer des forces de masse et/ou des couples de masse d'un moteur à combustion interne, comprenant au moins une section à balourd (2) avec un centre de masse (4) s'étendant de manière excentrique par rapport à l'axe de l'arbre (3) et au moins un tourillon de palier (5, 6) en vue du support sur palier radial de l'arbre d'équilibrage (1) dans le moteur à combustion interne, la section à balourd (2) et le tourillon de palier (5, 6) étant fabriqués séparément en matériaux différents et étant ensuite assemblés axialement l'un à l'autre au moyen d'une connexion rigide en rotation à goupille et alésage, caractérisé en ce que la connexion à goupille et alésage est réalisée en agissant par engagement par coopération de formes dans le sens de rotation de l'arbre d'équilibrage (1) et présente au moins deux goupilles (8, 9, 10, 11) et des alésages associés (12, 13, 14, 15, 16, 17, 18, 19) qui s'étendent de manière excentrique par rapport à l'axe de l'arbre (3).
  2. Arbre d'équilibrage (1) selon la revendication 1, caractérisé en ce que le matériau du tourillon de palier (5, 6) est un acier pour paliers à roulement, le tourillon de palier (5, 6) servant de piste de roulement intérieure pour les corps de roulement d'un palier à roulement.
  3. Arbre d'équilibrage (1) selon la revendication 2, caractérisé en ce que le tourillon de palier (5, 6) présente une largeur variable sur sa périphérie dans la direction de l'axe de l'arbre (3), de telle sorte que le tourillon de palier (5, 6), dans une zone de charge dans laquelle le tourillon de palier (5, 6) est sollicité par la charge radiale de la section à balourd (2) tournant avec l'arbre d'équilibrage (1), présente une première largeur (28) et, à l'extérieur de la zone de charge, soit nettement aminci en présentant une deuxième largeur (29) ou soit interrompu au niveau de la périphérie, les goupilles (8, 9, 10, 11) et les alésages associés (12, 13, 14, 15, 16, 17, 18, 19) étant excentrés par rapport à la zone de charge.
  4. Arbre d'équilibrage (1) selon la revendication 3, caractérisé en ce que les goupilles (8, 9, 10, 11) et les alésages associés (12, 13, 14, 15, 16, 17, 18, 19) s'étendent complètement à l'intérieur de la première largeur (28) du tourillon de palier (5, 6).
  5. Arbre d'équilibrage (1) selon la revendication 1, caractérisé en ce que deux tourillons de palier (5, 6) réalisées de manière identique sont prévus, lesquels sont assemblés aux deux extrémités longitudinales de la section à balourd (2), le tourillon de palier (5) assemblé à une extrémité longitudinale du côté de l'entraînement de la section à balourd (2) et un élément d'entraînement (7) de l'arbre d'équilibrage (1) réalisé séparément de celui-ci étant ensuite assemblés axialement l'un à l'autre au moyen d'une connexion supplémentaire rigide en rotation à goupille et alésage et la connexion supplémentaire à goupille et alésage étant également réalisée en agissant par engagement par coopération de formes dans le sens de rotation de l'arbre d'équilibrage (1) et présentant au moins deux goupilles (20, 21) et des alésages associés (12, 14, 22, 23) qui s'étendent de manière excentrique par rapport à l'axe de l'arbre (3).
  6. Arbre d'équilibrage (1) selon la revendication 5, caractérisé en ce que les connexions à goupille et alésage et la connexion supplémentaire à goupille et alésage présentent à chaque fois exactement deux goupilles réalisées de manière identique (8 et 9, 10 et 11, 20 et 21) et des alésages associés (12, 13, 14, 15, 16, 17, 18, 19, 22, 23) qui s'étendent par rapport à un plan de symétrie longitudinale (26) de l'arbre d'équilibrage (1) formé par l'axe de l'arbre (3) et le centre de masse (4) de la section à balourd (2) de manière essentiellement symétrique spéculaire.
EP09764783.8A 2008-12-02 2009-11-30 Arbre d'equilibrage Not-in-force EP2373908B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810060084 DE102008060084A1 (de) 2008-12-02 2008-12-02 Ausgleichswelle
PCT/EP2009/066061 WO2010063677A1 (fr) 2008-12-02 2009-11-30 Arbre d'équilibrage

Publications (2)

Publication Number Publication Date
EP2373908A1 EP2373908A1 (fr) 2011-10-12
EP2373908B1 true EP2373908B1 (fr) 2014-11-19

Family

ID=41665680

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09764783.8A Not-in-force EP2373908B1 (fr) 2008-12-02 2009-11-30 Arbre d'equilibrage

Country Status (4)

Country Link
EP (1) EP2373908B1 (fr)
CN (1) CN102239347B (fr)
DE (1) DE102008060084A1 (fr)
WO (1) WO2010063677A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010046163A1 (de) * 2010-09-21 2012-03-22 Magna Powertrain Ag & Co. Kg Massenausgleichseinheit
DE102010049897A1 (de) 2010-10-28 2012-05-03 Schaeffler Technologies Gmbh & Co. Kg Massenausgleichsgetriebe und Verfahren zu dessen Montage
DE102016202109A1 (de) 2016-02-12 2016-12-22 Schaeffler Technologies AG & Co. KG Hubkolbenmotor
US10663033B2 (en) 2017-07-12 2020-05-26 American Axle & Manufacturing, Inc. Balance shaft having reduced mass and inertia
DE102018106765A1 (de) 2018-03-22 2019-09-26 Schaeffler Technologies AG & Co. KG Unwuchtwelle

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4412476A1 (de) 1994-04-14 1995-10-19 Otto Michael Militzer Ausgleichswelle
DE19830051C1 (de) 1998-07-04 1999-11-25 Bauss Hans Werner Ausgleichswelle
ATE270403T1 (de) * 1999-10-19 2004-07-15 Magna Steyr Powertrain Ag & Co Ausgleichswelleneinheit für hubkolbenmaschinen
CN2496729Y (zh) * 2001-09-04 2002-06-26 王学建 汽车平衡轴
DE10349201A1 (de) * 2003-10-23 2005-06-02 Daimlerchrysler Ag Massenausgleichswelle einer Hubkolbenbrennkraftmaschine
DE202006020559U1 (de) * 2005-10-13 2008-12-18 Schaeffler Kg Radiallagerung
DE102007009800A1 (de) 2006-04-18 2007-10-25 Herzog Intertec Gmbh Ausgleichswelle
DE102006051996B4 (de) * 2006-11-03 2010-04-01 Magna Powertrain Ag & Co Kg Ausgleichswelleneinheit
CN201021705Y (zh) * 2006-12-22 2008-02-13 重庆宗申技术开发研究有限公司 发动机组合式平衡轴

Also Published As

Publication number Publication date
CN102239347B (zh) 2014-07-30
EP2373908A1 (fr) 2011-10-12
WO2010063677A1 (fr) 2010-06-10
DE102008060084A1 (de) 2010-06-10
CN102239347A (zh) 2011-11-09

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